Axial flow gas turbine having reheating means and specially shaped rotor and stator blades to provide isothermal expansion



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E HAVING REHEATING MEANS AND TO PROVIDE ISOTHERMAL EXPANSION fZ/I/VE' FPO/YT SPECIALLY SHAPED ROTOR AND STATOR BLADES W! -l- QC F AXIAL FLOW GAS TURBIN FUEL G145 May 19, 1953 Flled Aug 11, 1948 y 9, 1953 H. M. PUTMAN, JR 2,638,741

AXIAL FLOW GAS TURBINE HAVING REHEATING MEANS AND SPECIALLY SHAPED ROTOR AND STATOR BLADES To PROVIDE ISOTHERMAL EXPANSION 7 Sheets-Sheet 2 Filed Aug. 11, 1948 Inventar; Henry MPatmanJr @qim Atqys.

May 19, 1953 H. M. PUTMAN, JR 2,638,741

AXIAL FLOW GAS TURBINE HAVING REHEATING MEANS AND SPECIALLY SHAPED ROTOR AND STATOR BLADES TO PROVIDE ISOTHERMAL EXPANSION Filed Aug. 11, 1948 '7 Sheets-Sheet 3 COMPRESSED FUEL AND GAS Inventor; Henry MPaZmanJv 4y q Q l A tag/s.

May 19, 1953 .6? H. M. PUTMAN, JR 2,638,741

AXIAL mow GAS TURBINE HAVING REHEATING MEANS AND SPECIALLY SHAPED ROTOR AND STATOR BLADES A TO PROVIDE ISOTHERMAL EXPANSION Filed Aug. 11, 1948 '7 Sheets-SheetA (T3) *(Tr) In van for: Henry MP1! imam 2 2- C2-- &3

A tqys.

y 1953 H. M. PUTMAN, JR 2,638,741

AXIAL FLOW GAS TURBINE HAVING REHEATING MEANS AND I SPECIALLY SHAPED ROTOR AND STATOR BLADES TO PROVIDE ISOTHERMAL EXPANSION Filed Aug. 11. 1948 7 Sheets-Sheet 5 PRINCIPAL EXPAND/N6 FL U/D COMPRESSED H6237 jljuam ar% 25 'E CM May 19, 1953 H. M. PUTMAN, JR 2,638,741

AXIAL FLOW GAS TURBINE HAVING REHEATING MEANS AND SPECIALLY SHAPED ROTOR-AND STATOR BLADES TO PROVIDE ISOTHERMAL EXPANSION 7 Sheets-Sheet 6 Filed Aug. 11, 1948 J New $07,".

2,638,741 G MEANS AND DES FLOW May 19, 1953 H. M. F'UTMAN, JR

S TURBINE HAVING REHEA APED ROTOR AND IDE ISOTHERMAL TIN STATOR BLA EXPANSION PECIAL SH TO PROV 7 Sheets-Sheet '7 Filed Aug. 11, 1948 Jnven ton Ienr y/MPazmnJr: Z5

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Patented May 19, 1953 AXIAL FLOW GAS TURBINE HAVING RE- HEATING MEANS AND SPECIALLY SHAPED ROTOR AND STATOR BLADES TO PROVIDE ISOTHERMAL EXPANSION Henry M. Putman, Jr., Champaign-Urbana, Ill. Application August 11, 1948, Serial No. 43,593

1 This invention relates to apparatus for use in the generation of power. concerns gas turbine power plants. A principal object of the present invention is to provide a practical power plant operating at the high efficiency of the Carnot cycle. A further object is to provide a turbine power plant of high efficiency and low weight. More specifically it is an object of the invention to provide a gas turbine so designed that the expanding working fluid remains at a constant temperature during its passage through the turbine blading--in other words, to provide a turbine which operates isothermally. I am aware that it has heretofore been proposed to cause isothermal expansion in certain parts at least of gas turbine installations; but no practical way of realizing isothermal expansion within the blades of the turbine itself has heretofore been devised. The present invention contemplates the proportioning of the passages between the blades of the turbine in accordance with the heat actually released within said passages. In other words, the invention contemplates a design of these passages so that they have that particular and definite shape which insures isothermal expansion of the fluid as it flows through said passages. The only practical way of expressing the constantly varying shape and dimensions of said passages is by the use of a mathematical formula. Although the invention is apparently most important in its application to gas turbines, thev general principle involved is useful in turbines operating with steam, mercury vapor or other One object of the invention is to providenovel apparatus wherein a gaseous medium is expanded. isothermally and in doing so creates mechanical energy. A further object is to provide a gas turbine which operates substantially on a pseudo- 11 Claims. (Cl. 60--39.1'7)

More particularly it I In the usual commercial gas turbine air is first combustion are expanded almost adiabatically through the turbine stages. In some cases reheating between stages has been proposed, for example in the Swiss Patent No. 88,624.

In accordance with the present invention the separate combustion chamber is preferably omitted and combustion takes place under isothermal conditions within the turbine blading itself. The gases enter the turbine uncombined and at a high temperature and pressure. They expand as they are burned and they come out of the turbine at a relatively low pressure. The expansion which takes place in the turbine blades is at a substantially constant temperature. The heat of the expanded gases coming out of the turbine is used to preheat the entering gaseous mixture to a temperature which approximates that of combustion.

The novel process of the present invention consists essentially in causing one or more fluids to evolve in a continuousmanner with constant input of heat while flowing through a passage whose transverse section so varies from point to point, with respect to the heat input at successive points, as to cause an isothermal expansion.

There is herein disclosed the way of establishing the shapes and dimensions of these passages so that isothermal flow is assured, particularly for the general case where the quantity of heat communicated to the flowing fluid in some function of the abscissa along the axis of the passage. This method enables one to establish the varying sections to be given to the passages, either to obtain combined combustion-expansion or a simple expansion, in either case isothermal.

Other and further objects and advantagesof the invention will be pointed out in the following more detailed description and with reference to specific examples and to the accompanying drawings wherein Fig. 1 is a diagram illustrative of a duct for the continuous flow of gaseous fluid and which is employed herein as a basis for certain definitions of terms employed; t

Fig. 2 is a view similar to Fig.1 but modified for use in the discussion of flow conditions when the duct is bodily moving, for instance, when the duct is defined by the moving blades of a turbine; Fig. 3 is a diagram illustrative of the proper shape of cylindrical duct for isothermal flow;

Fig. 4 is the entropy diagram for a turbine embodying the present invention;

Fig. 5 is a fragmentary diagrammatic vertical section, partly in elevation, illustrating an internal combustion turbine power plant in accordance with one embodiment of the invention;

Fig. 6 is a view generally similar to Fig. 5 but illustrating a turbine wherein numerous small burners are arranged within the blading in such a way that the burning gases are separated from expanding gases, the blades themselves bein hollow so as to house burners, or, alternatively, to convey "hot burned bases from "a centrally located combustion chamber or furnace;

Fig. '7 is a view generally similar to Fig. 5 but illustrating a turbine wherein heat is added to the flowing gaseous fluid durin expansion by the use of a secondary circulating superheated fluid,

for example mercury vapor;

Fig. 8 is a view generally similar to Fig. 5 but illustrating a turbine wherein heat is added to the flowing gaseous fluid during expa-nsiomby the use of a secondary circulating superheated fluid heated by burners and flowing through the stationary blades;

Fig. 9 is a diagrammatic end elevation of a turbine embodying the present invention;

Fig. 10 is a fragmentary diagrammatic -;side elevation of the turbine of Fig. 9;

Fig. 1-1 is an edge elevation of a turbine blade constructed in accordance with the present invention;

Fig. 12 "is a front elevation :of the blade of Fig. ll; and

13 is a diagrammatic section, for example onthe plane of line =l3|3 of Fig. 12, illustrati-ng the shapes of a pair of adjacent turbine blades made .in accordance with the present in- Mention.

*In the following discussion it will be shown that it is technically possible so to shape the how passages .of a gas turbine with respect to the heat supplied as to insure a constant temperature of the flowing fluid. It will also be shown how -.to arrive at the proper shapes of the fluid passages. Since these .shapes are best defined in terms of mathematical equations, resort will :be :had :to this method of disclosing the invention.

In the :following discussion, :reference is made to Figs. '1, 2 and 13 and the following definitions are employed:

a: is the abscissa of the running section taken along the axis of the duct.

:Cis the mean velocity'of the gas at the running section; .for purpose of simplification .the gas is supposed homogeneous and this velocity is supposed uniform in this section. (C is-a .function of a.)

Cu is the mean velocity at the entrance of the duct.

P is the discharge from the duct, that is to say, the quantity of fluid passing through the duct per unit of time, a known constant quantity.

(ta: isthe quantity of energy trans-formed into heat by .iriction loss. (A suflicient approximation considers g constant.)

1) is the specific volume of the gas in the running section. (,1: is a function :of mg) m-is the pressure of the gas in the running section. (P is .a .function of m.)

T is the absolute temperature of the gas in the running section. The ,gas is supposed to be ;a perfect gas. (T is also -a function of 112:)

:R \is the gas constant.

S is the area of any chosen section, here referred .to as the running section. (-8 is a function .of ax) 1S is the area of the entrance to the duct.

9 is {the acceleration due to gravity.

m is the pressure at the entrance to the duct.

A relation may be derived between the above quantities which enables one to find experimentally-the proper area to give to any chosen sectionand thus to determine the form to be given to :theduct in order that the flow be isothermal.

The equatioHS of .flow are:

c o0 irat ZJU=RT [3] fByderivation withrespect to a and by elimination,

This is a differential equation of the first order with respect to C which enables one to find the velocity 0 in terms of a functionof the abscissa -:1:. :C being known, one is able to find a; in terms of a function of x from [2] and p in terms of J: from [33.

If the cumulative quantity of heat communicatedto the flowing gas v(from the jn-itial section at the entrance of the duct up to the running section at abscissa 2:) is named q (r), a function of .72, this quantity is related to the above values ,by the equation:

Where A is the caloric equivalent of work and where Z is the entropy which can be evaluated from the entropic diagram, .or computed from the following formula valid for perfect gases:

Z: 01, lognp-l-C lognv Equation 4 above shows that in the general case of steadyflow all the physical variables of the flow may be computed if one knows for each section the temperature (supposed to be uniform in the section) and the area of the section.

This method makes possible the experimental study .of all flows where the heat communicated to the flowing fl d is a function of the abscissa along theaxis of the flow. Such flowmay be a jet, difiusion flame, continuous combustion, or continuous reheating. By this method one is able to find the appropriate sections and areas for a duct in order thatjfor a givencommunicated heat the flow maybe isothermal and also to measure the communicated heat from a given jet, diifu- .sion flame, or continuous combustion in a given duct; itis sufficient to measure the temperature in each section and to know the area of each sec- The conditions vfor isothermal fiow are:

from which can be derived This last Equation 6 enables one directly to find the running Area=S (w) of the duct in terms of a function of the communicated heat q=q (as) so as to insure isothermal flow. This equation also holds for a moving duct, providing the movement of the duct is pure translation, that is to say, all points in the duct have the same velocity relatively to a fixed axis.

However, with reference to a moving duct, the value c in the formula must be recognized as a relative velocity, that is to say, the velocity of the fluid relatively to the moving duct. Moving turbine ducts, blades or buckets may be treated thus, providing the stream of fluid is thin and sufficiently short, relatively to the distance between said part and the axis of rotation of said part.

In the general case of a turbine where the above conditions are not realized, the following equations may be used in finding the proper cross-section of the duct to insure isothermal flow, reference being had to Fig. 2 of the drawings: C C

I "Li q-l-Agw AL Vdp A g+rv +AW... where Ww is the work delivered to the wheel between the entrance section and the running section (x) FE w #0 o a Where a is the vectorial value of the reltative velocity; 3 is the vectorial value of the absolute One embodiment of the basic principle of the present invention is diagrammatically illustrated in Fig. 5. In the turbine power plant shown in these views, the uncombined gaseous fluids, for example, atmospheric air and a combustible gas, are received at the low temperature To and compressed, passing from the initial state (0) the state K to where their pressure has increased to a value p. The temperature is kept as low as possible during compression but does rise to a value T1. This operation is done in a compressor 1, preferably a rotary compressor. Preferably, though not necessarily, the compressed gases are passed through a heat exchanger 2 where they are heated to a high temperature T2 by the hot exhaust gases from the turbine. The highly tionary blades.

'perature increases slightly to value T1. process of compression a quantity of heat, meastion or combustion may raise the temperature to.

a higher value T3 before the isothermal process begins.

The gases then expand in flowing through the turbine passages, while at the same time the combustion progresses but the temperature is maintained constant due to the form of the blades and the interblade ducts. Various means may be employed in order to insure continuous combustion inside of the blading.

One method is to employ diffusion flames inside of the blading. The hot compressed gases fiow first in parallel streams, as shown at I l and I2 in Fig. 5. Combustion starts at l3 and continues along the difiusion flame fronts [4 which move through the ducts between the stationary blades [5 and rotating blades l6 of the turbine.

The sign p. is a vectorial representation of the velocity of therotating blades and is intended to distinguish the rotary blades I6 from the sta- C'ombustion is regulated so that it ends in the last part of the blading and the expanded burned gases flow out of the blading at substantially the same temperature as at their entrance to the blading. The burned gases communicate their heat to the unburned gases in the heat exchanger 2 before leaving the power plant at a temperature T5.

Fig. 5 is intended merely to disclose the characteristics of operaiton and the principle of construction. The structural parts composing turbine and turbine power plant are substantially like those of existing gas turbines. Differences in construction are principally directed to the addition of the necessary pipes and ducts to conduct the fuel to the entrance of the turbine, blading, the addition of a set of burner orifices designed to start chemical combination just before the gaseous fluid enters the blading and passages shaped in accordance with the invention In Fig. 4 the entropy Z of the idealized working fluid is plotted against its absolute temperature T. In the diagram the intake is at the point 0, compression takes place between I] and K isobaric heating in a heat exchanger between K and K combustion starts at K isothermic expansion between K and K isobaric cooling and heat exchange between K and K and optional exhaust between K and 0. The working fluid is taken at atmospheric pressure and temperature To. This is referred to as the start (ll) in Fig. 4. The working fluid undergoes polytro-pic compression. Its entropy is decreased and its tem- In the ured by the area K t/[ 11 0, is abstracted from the working fiuid. This takes place preferably in a rotary compressor. From state K (Fig. 4) the working fluid is heated at constant pressure to the high temperature T2 in the heat exchanger. The quantity of heat supplied to the working fluid during this isobaric exchange is measured by the area K M M K (Fig. 4) and is supplied by the exhaust gases. This area is equal to area K M M K (Fig. 4) less the heat losses in the heat exchanger.

From state K (Fig. 4) at the outlet of the heat exchanger, the working fluid undergoes optionally a superheating process from state K to K in special ducts just in advance of the turbine blading. This brings its temperature to a value =ptionally this .superheating may be em;- ployed toincreasetthe lvelocity of the fluid.

state K :to (Fig. .4) the fluid under.- goes :both continuous heating and expansion in the turbine :b'lading. The wheat supplied to the fluid :from state K to state K is measured by the area K M M K I Z K and is all available :as mechanical work. This heat can be supplied in various ways. Eur example, suppose the working fluid is composed :of two gases react chemdually with evolution of heat and the combination is gradual as :the gases pass through the :blading. At the exhaust or the turbine, the working fluid is at substantially thesa me temperature .asat-athe entrance but at a lower pressure. This is referred :to as state and rTAFTs). From the exhaust .of the turbine the working fluid is :led to the heat exchanger and communicates its heat content to the entering fluid. Thedii'f-erenceof temperagture A (Fig. 4) expressed .as T4=T2 is calcuiated to permit the necessary quick exchange of heat in the heat exchanger. 'Ilr qnantity of heat exchanged is measured by the area Ktlllildfifi .equal to area K' M M- K from state K tostate K th so rma exp nsion i rep e nted o the entropic diagtam .(Eig. d) by agStraig-ht line.

pifiusion flames inside of the blading of the turbine may be employed .as previously disclosed. The m hod {o c m a n t f n t e p o e ,form to a duct for a di-ifusion flame so that the flow inside the duct may be an isothermal expansion can be derived from readily available literature.

In a second embodiment of the invention, the .bla-ding and th ,interblade ducts of the turbine are provided with a number ,of small burners I! very .s' ;ilar to small Bunsen burners, as diagrammatically illustrated in 6. In this arrangement the flow .of air is divided, the two divis ns bein f -r d t as rimar e =ondary air. The general thermodynamic cycle tollowed by the secondary air, on the one hand, and the primary :air and fuel gas, cm the other hand, is in general that "illustrated in Fig. .4. However, the temperature of 'both primary air and fuel gas is kept low enough so that chemical combination is avoided before they reach the burners. The compressed fuelgas and the compressed primary air are mixed and delivered by pipes 12 to a series of small "burners ll in the stationary hollow blacling it burners, the heat released by each one, and the relative disposition of the burners are so designed that the Working fluid in the turbineblading undergoes isothermal expansion.

The number of Referring to Fig. :7, which illustrates a, third specific embodiment, the working fluid is first compressed at l and then passes through a heat exchanger 2. The hot compressed fluid .is then expanded and at the same time supplied with additional heat by a system of thin Walled metallic pipes Ni and 2| which convey a reheating fluid. Preferably, although not necessarily, the pipes I5 constitute the stationary blades of the turbine and which correspond to the stationary blades l5 of Figs. 5 and 6. The number of reheating tubes and their disposition and the-temperature of the reheating fluid is such as to provide an isothermal or substantially an isothermal expansion within the blading. The turbine emplayed in accordance with this modification is basically like a conventional steam or mercury vapor reaction turbine, but with the addition of .a reheating system comprising pipes endthespe- .cial reheating tubes 1'5 and :2] within the blad- .ah sh t mpe tu n wh ch con ey a per ea ed fluid p efera ly a heavy fluid, having a high specific heat and high heat conductivity; this arrangement also requires the addition of a separate reheating plant P (Fig. '7) for the separate reheating fluid. As suggested, the stationary blades 15 may be made hollow and themselves constitute the ducts for the reheating fluid.

Fig. 8 illustrates a fourth specific embodiment air/herein continuous or quasi continuous reheating during expansionis obtained by providing the turbine blading with a chemically distinct reh at n circu c rr ns r eat fluids a s The reheating may also .be provided by two fluidslin the process of combination. This realization of the invention may ,be .used in steam turbines, mercury vapor turbines and inigeneral in turbines using any vapor.

The principal expanding fluid, fuel ahdcomburent undergo compression separately and pass through the heat exchanger. The fuel is optionally mixed With primary air ill-suitable mix- ,ers X similar inldesi gn to carburetors. The fuel isthen conducted to a series of small burners H inside-of the separate secondary air circuit. This separate comburent circuit is defined by metallic pipes. .Qbviously the stationary blades 5 them. selves may .be hollow and thus define the desired air passages. The principal expanding fluid is reheated-eitl-ier alone by conductivity as it passes between the hot metallic bladesor pipes 15 or by ,conductivity combined with mixing effect and radiation. The number of reheating tubes and burners and the heat released in each one is so designed as to insure a quasi isothermal flow inside the blading. The turbine employed is basically like a steam or mercury vapor reaction turbine but with passages shaped in accordance with the present invention, and with the addition of -a reheating circuit system comprising pipes to convey fuel and optionally primary air, on the one hand, and gcombpurcnt, on the other, and a set of metallic blades or pipes l5 properly shaped and which transmit the heat released by combustion or part of it to the expanding fluid flowing around them. This arrangement further comprises a set of small burners ii located in the reheating :tubes or an :integrant part of them, and optionally aset of mixing devices X .to the ,fuel and the primar air, such mixing devices being in the nature of carburetors. The fluid. expanded in the turbine may be air or othergas- .eous fluid, preferably aheavy gas, which is chemically inert, such as argon or a suitable vapor, such .as ordinary steam, or preferably ,a heavier vapor. The use of vapor instead of a gas is very advantageoussince it saves the work or compression. In the .case where the fluid that does the expansion work. is a more expensive fluid, the circuit is .closed .so that the same body of nuid remains in the circuit, being first expanded and then cooled and re-compressed or re-vaporized.

In .the case .of the realizations cf the invention in which burners discharge into the passages, all the heat available from combustion or chemical combination is released at a constant tempera- ;ture which can be very high and immediately transformed into mechanical energ in the ,form ither of velocity energy communicated to the fluid, in the case of a stationary duct or nozzle, or either velocity energy and work on the bucket by reaction in the case of a rotating duct or bucket. The energy of chemical reaction thus directly available in the form of mechanical work, that is the power of fire .(as used in Carnots works) is thus completely converted into power for useful mechanical work.

If the work of compression can be avoided, for instance by using a vapor that is vaporized under pressure by heat, all the heat communicated to the working fluid at high temperature is transformed into mechanical energy available on the shaft of the power plant for use outside; the amount of heat necessary to vaporize the working vapor is not reproduced in the form of mechanical energy but remains in the form of heat that can, however, be optionally used in an outside heating system.

Illustrative examples of the design of an isothermal noezle in accordance with the present invention.

As here employed, the term nozzle is to be understood as designating any passage, for example the passage defined by adjacent blades of a turbine stator, through which an expansible fluid flows while it expands isothermally.

Assume a fluid composed of a mixture of perfect gases having a gas constant 42.5 K cal. kg.

so that the corresponding compression ratio is The effect of friction is neglected.

The distribution of the heat communicated to the fluid is as follows, asreferred to lengths of duct beginning at the entrance section and terminating at the following distances from the entrance section:

Distance=0.5' 3 of the total heat Distance=1.0 38.8% of the total heat Distance=2.0 56.4% of the total heat Distance=3.0 68.8% of the total heat Distance-=40" 77.8% of the total heat Distance=6.0" 98.2% of the total heat -Distance=6.2 100% of the total heat The above figures indicate the heat released by a diffusion flame resulting from .interdiffusion and combination of a central flow of methane gas of circular cross-section, which at the entrance tothe duct is 0.2 inch in diameter and which forms the axial core of an annular stream of air, which at the entrance to the duct has an outside diameter of 0.4 inch.

Both, streams of gas are at a temperature of 900 K. and have an entrance velocity of 23A meters per second. Both the methane and air are diluted with nitrogen to an overall dilution of 11.6%. The total heat of combination is thus 85 K cal. kg.

the first one-half of which is released in the isothermal duct, andthe second half after the gas leaves said duct. The above computations have been made in accordance with the above formula and from data given by Burke as it is found in a book entitled Combustion, Flames and Explosion of Gases, by Lewis and Von Elbe, Cambridge University Press, Cambridge, 1938.

However,this distribution of heat may be determined experimentally.

The duct here chosen for consideration (Fig. 3) is of circular cross-section to correspond to a flame of that section. However, this is merely by way of example. The same kind of computation applies to the design of ducts of such other sections as might be desirable. The circular section is very useful as an example, and is particularly useful when a multiple burner is employed. Preferably, in such a compound burner, the individual orifices or jets are of circular section and located at the lattice joints of a centered hexagonal lattice. Thus, each individual burner jet is surrounded by a hexagonal space which is roughly approximate to an equivalent circular space tangent to the sides of the hexagon. Thus, each burner approximates a circular jet burner surrounded by an annular mantle.

In the following discussion, the following assumption is made, to wit, that all of the heat released by combustion at one cross-section is communicated to the fluid at a cross-section located at a constant distance of 0.125" ahead of the cross-section at which the heat is released.

The computation of the successive sections of the duct may be'made by the use of Formula 6 or by the use of combined Formulas 2 5 and 5.

For air kg. m. R-2927 kg. m.

427 kg. m.

K cal.

K cal. I

For

2gRT=516600 m2 for the data of theexample given, corresponds to a compression ratio 1r= g 4 and the value Aq K cal 2 42.5 kg. corresponds to a compression ratio As the burned gases, the example given, are discharged into the atmosphere, the pressure of the gas at the entrance to the stationary ducts assays r Let D =the diameter 01- the running sectionof the duct at any given point, and let s21 1 s D The following table gives the values of A 6 C 4%- 2 l s c 71' andz for sections of the duct at a series or points measured in inches from its entrance end;

ne'g' lect this latter release" of energy and shape the blades like those of an impulse turbine; a more careful approximation requires that the blades be shaped as though it were a reaction turbine. I

After leaving thefirst wheel, the burning gases expand from a pressure of about 2.0 atmospheres to a pressure slightly above" 71.0 atmosphere in a second stage, in passing through a stationary duct or nozzle; The shape of this latter duct or nozzle is such that the expansio1i' combina tion process is isothermal, the method of computing the shapes of the passages being same as that above described.

In passing through the second stationary duct or nozzle, the velocity of the fluid is greatly inexhaust fluid is led through the heat exchanger and communicates its heat to the entering compressed fluid, isfinally' discharged to th atmosphere. I

The first stationary noz'ze is here designed in accordance with the following method of com putation, completely equivalent to the direct use of Formula Neglecting frictionpa heat input of K cal;

corresponds to a release of kinetic energy t iens tie-re AE- --427 X425 kg -l8150 kg- 1 s1-50=hse= 3e; sec.

sec. sec: sec.-

0:597" sec.

I I 02 log 7r= S D 04 I qp A02 a z 0 Inches cent mfl/sec. COLE/3C2 m./scc. m .5 D 7 0 550 23.4 0 1 1 1 0.40 10,700 1 1, 250 10 0 0.021 1.02 4. 42 2.10 0.10 117,000 117,550 343.0 0.2 7 1.25 12. 3.40 0.118 197,050 198,050 445.0 0.300 1.48 I 12.85 3.58 0:112- 245,800 246,350 400.0 0.470 1.01 13.10 3.02 0.1105 278,000 278,550 528.0 0.533 1.71 3.20 3.035 0.1100 360,000 350, 550 592.0 0.680 1195' 13.00 3. 605 0:ll l0 350,100 350,050 597.0 0.503 2.0 12.80 3.58 0.111s

occurs. As a rough approximation, one may 2:; The above condltions for communicated heat distribution can be obtained by providing the nozzle with one hundred difiusion flames arranged-equidistantly from one another, as above described. This can. be accomplished by arranging at the entrance to the fixed duct or nozzle 2. burner consisting of 100 cylindrical jet tubes each of 0.2" in diameter with their centers disposed at the lattice joints of a central hexagonal lattice.

In another example, inall respect similar to the above one, the heat supplied to the working fluid during isothermal expansion is produced by four sets of 400 diffusion flames, each, burning inside of the working fluid. The great bulk of this working fluid is nitrogen. The burning gases that supply the heat are methane (CH4) and oxygen (02) diluted.- in the bulk of nitrogen; both methane and'oxygenconstitute a minor part of the working fluid, together with the products of combustion which are carbon dioxide (CO2) and water vapor (H2O).

In the computations which follow, the'worl z-ing fluid is treated as having all of the characteristics of ordinary air, so far asits thermodynamic properties. are concerned, and this is usually a. satisfactory assumption.

Figs. 14 and 15 diagrammatically" illustrate a turbine embodying the present invention. As illustra't'ed} the turbine comprises a shaft 40' which may, for example, be coupled directly to the shaft of an electric generator. The shaft 40 carries the rotors of two wheels 41 and 42', each rotor being" arranged within a stator housing, and each rotor having blades which cooperate with the fixed nozzles of the stator. Four first nozzles=43 44 45 and 46 are arranged to deliver the expanding fi-u-i'd, for example, a-- combustible gas, to the first wheel 4|, the nozzles 43 44', etc. being arranged 90 apart. Exhaust from the'first wheel is delivered to the second wheel 42' by second nozzles t! which may be similar to the nozzles 43,40,- etc The exhaustfrom the turbine 02 is delivered by a duct 40 to a heat-exchanger 4%. The conduits 5| and conduct combustible fuel gas and air in heat-exchanging relation to the exhaust flowing through the heat-exchanger chamber, and the preheated fuel gas and air are then delivered tothe nozzles- 43, 4 4, etc. For specific example, methane gas, diluted with nitro gen, with a dilution ratio of 0.0466 (that is, a mixture of 4.66% by volume of methane and 95.34%

"13 by volume of nitrogen), flows out of a compressor at a pressure of 4.0 atmospheres and at a temperature of 27 C. or 300 K. This gas is conducted through the heat exchanger 49 wherein the temperature of the gas is increased to 627 C. or 900 K. while its pressure remains substantially constant at 4.0 atmospheres. From the heat exchanger (whose detailed construction forms no part of the invention) the diluted methane gas passes through four cylindrical conduits each of 2.0" internal diameter, and at a velocity of 23.4 meters per second. Each of these conduits 5| are arranged inside of a 4.0, diameter pipe 50 through which flows diluted air. The methanecarrying conduits lead to a distributor 53. This distributor divides the diluted methane and delivers it in substantially equal quantities into 400 pipes of circular cross-section and of 0.1" diameten, Preferably the cross-section and arrangement of these 0.1" diameter pipes is such as to produce a compact hexagonal network. The velocity of the diluted methane gas in passing through the 0.1" diameter pipes remains at substantially 23.4 meters per second. A mixture composed of 3.1% of oxygen and 96.9% of nitrogen can be obtained by diluting air in nitrogen, the dilution being 0.155. This dilution of oxygen is calculated to produce a stoichiometric ratio between methane and oxygen according to the following formula:

CH4+2Oz- CO2+2H2O+210.0 Cal.

The total discharge of the diluted methane plus diluted air in the four sets of 400 streams is 0.764mfi/sec. These streams of diluted methane start burning in the air in the first isothermal nozzles 43, 44, 45 and 46. Combustion continues through the first wheel 4| and in the second isothermal nozzles 41. Combustion is complete at the end of the second nozzles 41 so that the second rotor is purely an impulse wheel.

The proper form for the first nozzles, so that the flow of burning gases may be isothermal, is obtainable as herein described. By properly dimensioning the device, the temperature will remain at 900 K. throughout the first nozzle. In the example new under discussion, the firstrotor of the turbine is of an axial width sufficiently small, as compared with the stationary nozzles, so that the effect of reaction due to combustion inside of the rotor 4| may be neglected. The rotor is an impulse wheel rotating in a space at a uniform pressure of 2.0 atmospheres. The blading of the rotor is shaped as in an ordinary impulse turbine, so as to provide for maximum efliciency and continuous flow. In another example, a method is disclosed whereby the proper form may be given to the buckets of a wheel,

inside of which the effect of communicated heat can not be neglected. The method of giving the approximate form to the second stationary nozzle is exactly the same as that disclosed at the first stationary nozzle. The method of giving the proper shape to the blades of the second wheel so that the efiiciency of this wheel may be a maximum is the usual method of design used for purely impulse turbine wheels.

During the operation, the pressure drops from 4.0 atmospheres to 2.0 atmospheres in the first stationary nozzle, and the velocity increases from 23.4 meters per second to 597 meters per second. In the first wheel the pressure drop is negligible. Neglecting friction and shaping the blading of this wheel for an absolute outlet velocity of 23.4 meters per second (the same as the velocity at 14 the entrance of this stage), the first wheel converts the velocity energy released in the stationary nozzle into mechanical work on the shaft. The velocity energy head is I l The total discharge is 0.764mfi/sec. in volume or 1.20kg./sec. of equivalent air. The power available on the shaft is 18150m. 1 .20 kg./sec.=21800 m. kg./sec.=290 H. P.- 216 kilowatts.

In the second stationary nozzle, the pressure drops from 2.0 atmospheres to 1.0 atmosphere and the velocity increasesfrom 23.4 meters per second, to 597 meters per seconddue to a heat input of 42.5 k calories from the second part of the combustion of the methane-the temperature of 900 K. remaining constant.

The second wheel rotates in a space which is at atmospheric pressure. The fluid leaves the wheel with an absolute velocity of 23.4 .meters per second (the same as the entrance velocity for the inlet of this second stage). The speed of the wheel is 14,000 revolutions per minute and the tangential velocityat the pitch circle of the wheel is 300 meters per second. Neglecting friction, this second wheel, converts the velocity energy released in the second stationary nozzle into mechanical work on theshaft which thus receives a power of 2X9.8l m./sec. I

1.20 kg./sec.=290 H. P.=216 kilowatts K cal./kg. 1.20 kg./sec.=l02K cal/sec.

The consumption of methane gas is 0.191 m. /sec. 0.0466=0.0089 m. =8.91/sec. (at

900 K. and 4.0 atmosphere) 10.751/sec. (at 0 and 1 atmosphere) or 7.75 gr./sec.=28 kg./hour Certain differences between the construction hereinabove referred to and that of existing gas turbine power plants may be noted. Thus, in the existing power plants, the combustion offuel takes place in an outside combustion chamber at about constant pressure, whereas, in accordance with the present invention, the combustion takes place throughout the nozzles and buckets of the turbine itself, with a great drop in pressure between the point where combustion starts and ends. In existing power plants the temperature rises considerably in the combustion chamber, whereas in the present turbine the temperature remains constant all through the combustion nozzles and bucketsof the turbine wheels thus, the expansion of the fluid is isothermal.

The following example relates to that situation where the heat communicated to the fluid, while passing through the blades of the turbine wheel, is not negligible in comparison with the velocity head of the stream approaching the wheel.

Assume a wheel having a pitch circle diameter of 16" or 40.7 cm.; a rotational velocity of 14,000 R. P. M. (that is; a tangential velocity at theitch cable 01 3'00 lit/S66). Also assume It is also assumed that the 16 This angle 2 at the outlet must he" rei ated t the angle 120 at the'iniet as expressed by the equation distribution of the communicated heat within the 5. Thus. and i=2? 1 ifi f 8 5 25 2: 2.332? to the fluid Havin'g' ascertained the ab' ve' value, there is: W .3 s 1 d d ig is thusd'raw'n'a curve Fig118in'dicatin'gthe central 4 3f fhmu path tangent at the entrances'ection' (0%) to'the" 25 g w g 5456f rotation vel'obity' at (inclined at 37) and tangent it;tumtas'aviifm 255s 1 11 23 3155 51 gg%;. g 1'; age 1 veoc ywi lnc 'ea 'emer second half of its pathand 70 1'; cm ai-ium- Chose? ebmply with ether requirements. v i w I 1' h a asmaxrum efficiency. At each of the p01 ts 351511 the fluid has tiaveied thrte-quarte1s 15 (01%" etc.) normal to the central Dam j .0 r 0 cuiveis diawitandon eachsideof'thecurve on'e h r s e of he w e ke 22 $331132 iitiififis if 513E305 irfiixitittiili i mined and from this data the wanjs of the'etitire" the delivery nozzle; the absolute velocity 00 of f} i f f i fg fifi $532: the fluid at the entrance (597' BIL/S801) and the the dnes of adjacent blades must we tangential linear velocity' i (300 m./sec.') of the 0 Wheel; the velocity diagram may be drawn, 26 1.75

from which may be determined the relative en"- trance ve1'0city 3 in magnitude and positio Thus, the position of the edges of theblade are 70.2330 From this point, the compw completely determined andthe-shapeof the blade t'atiori of the areas of the duct at any selected sec- F be f located at tion is exactly the same as the computation for 30 g z' of 1175 about the P of the a stationary duct. W as Upon the assumption that the fluid entering In the foregomg example the helght of the the bucket is t compressed at 9000 K. and bu'cket a Variable, Variationlinear at 420 atn1ospheres-"-neg1'eeting frict'i0na heat across the Wheel and Such that input of h 1.6 Kcal. 1 n e'aoe'xpe er 'eeas p1 425 kg I th' b'v eaml whethhtupl ed to the Working fluid during isothermalexpansion corresponds to a release of kinetic energy accord" is produced by four sets of four hundred diffusion ing to the formula 40 flames burning inside of the working fluid, the 2 2 k K I k greatbulk of the working fluid is n trogen. The =l 7 a111- X 41.25 $5 g burning gases which su ply the heat are methane 0 K ee- (CI-T4) an o'xyg'er'r ('02) diluted mthe ma s or 2= 2 ':2 (9, 1 nitrogen, the methane and oxygen alsoconstitut'e' kg m 45 a m'ir'ronpart" of the Wo'rkir'igfiuid, tdgeiihel with (1815 ')==35,605 mF/sec? the products ef earn-15115111011 Which ar'e carbon di oxijde (conamiw'aterv'apor(1120) The values of In cases where the quantity of heat 0011111111111 dated to the flowing fluid can not, Within per 2 7 P0 .Zo NW0 v 'Y; 5; =7; i'n-iss'ible'approximation,- be regarded as'unifoi'mly v communicated toall points in a given Gross-set:- (wh'ere W the width" of the bucket, axially of tionof the flowing stream, the fouewmg method the Wheel) are for sections" located at paints may be'ns'e'df which are 0%; 25%; 50 75% and 106% of Divide the stream into a number of fillets to the'path from the entrance section. eaclr of which heat is communicated 11111161 11119 L fi Percent A in I 2 ye "'Y 10211 1r B" Z CHGfi' hP 2 K0 of pat percent raj/sec. mJ/sec mJsec. l iofybuiwt)v W .mches (mm.)

d Ct 'r'1e cogdgtion oifJhproinerhdesi'gn tha; Ellie .thrgugh the cross-seet i ofi. Inorder that the heat s ance e Wee 1 ISO e e 363 0 8 0210 was may be isot "er'maL each individual glatdes B71;d a d B g adlmhbe the game is :Ee 7 iiiit must have a cross-sectional area according is ance eween' e isc arge e ge o e he formula blades. This distance is represented by the WA equation *AR C H W S0 0 2 2 n a 78 v q pv=RT For gases whichrdo notifollowttheilaw oi periect gases, an approximationiinithe design otthetturbine passages may be made by the use of'tVa-n-fder Waals formula, that is to say,

.In this formula the valuesmandcof the-perfect gas "are replace'd by and (v b) respectively.

=-When-her-ein 1 reference is made i to 1 a gas turbine it is to be understood that this termis used in the broad sense to mean any:turbine orrequivaierit apparatus *working with any gaseous fluid whether simpleorcornpoimd and whether:a pure ,yg-as a nii-xturaoi pure gasesiavapor or avmixture of' a gasand vapor.

1. A prime movertcomprising;asrotorhaving,a series ,ofiperi'pheral blades idefining fluid passages, and means defining a duct through which a burning gaseous mediumtfiowsttowardtsaid-fluid passages.saidductbeing shaped and; dimensioned in accordance" with the-formula where g is the accelerationdue to gravity, "Co isthemean-velocity attheentranee k-to tithe duct,

*R- is thegasconstant, T is the absolute "temperature-Of? the gasxatathe chosen section,

e is the base of the systemof Napierian logarithms,

r is the abscissaof' the"chosen-section-measured 1 along the. axis of the'duct,

its is the" quantity "of energy-transformed into heat by friction loss,

q is the quantity of heat communicated to the flowing gas from entrance section to chosen section,

A is the caloric equivalent of work,

So is the area of the entrance to the duct, and

S is the area of the chosen section,

ing burners interposed between the blades of the,

T8 stator th-roug'h Whichdourning gaseous medium is delivered into the spaces bet-ween fthe stator blades said spaces qcollectively --consti,tuting fthe duct wherein isothemal"expansion takes place. "4. A prime "mover according to :claim ,1, rurther characterized in having a stator provided with spaced :blades, coaxial with the r or, the spaces between the stator blades "collectively constituting the duct,in which isothermal expan- 10 sion takesplace, and heat-exchangermeans constructedand, arranged-i0 utilize thePheat of the fluid medium "escaping "from the motor *for premeatins thee-gaseous im idimncnniits W r-i 2 ssai duct.

5. A prime mover according int iclaim :1, iii-u ispacesihetweengtheestator b c ie ollestiv lrtccn- :stituting ithe -.;duct whi h iisothermal esp n- --sion ttakes ipiac rthe ,hlades n 'ithe es te as hollow, andrme ns ferrintroducm a heatin medium into the hollow,,blades thereby to add heat energy to the gaseous medium flowing through the ;,.duct.

6. A prime,mover;according to claim 1, further characterized inhaving a stator provided with spaced blades coaxial with the rotorpilihe spaces betweenthe statorblades collectively ,contsti ne the .,.duc in which i dl herma t ens-I o sion takes place, the blades of the statorbeing hollow, and having burner oliifiqesilpm {which lflamesissueri r, add nstheatinscenergy:t aseous medium flowing through thefluct.

J1. A ,prime mover,.,.ac.cordin to claim All, Jurther characterized in having a stator proyided twithtspaced @hlades, coaxial w th th QtorQth pa tw t statcr,blades.colleetivelmc ,stitu-ting the ,duct 1 in which; isothermal :expansion takes place, thin walled,, llollow,pipes ex- 1tending through,spacesbetween,thasta d tb afies,

and meansfondeliverin a heati almedium i said hollow pipes thereby to add heat energy to the gaseous medium .flowingihroughthe duct. ",8. .-A -,prim m ter accordin ,t ,,c1aim 11L311!- ther characterized.,in..,harinstarstator .prwided with spacedblades coaxial with the'rotor, "the -spaces 'betweenfi'thestator blades;collectivelwconstituting 1 the duct tin --which isothermal a expansion-= takes -;-p1ace, thinewalled, hollow gpipesaextending 'through spaces between 'tthe sstator blades, and means for heating and circulatingta heating--mediumthrough said pipes' thereby to add heat-evenly tor the -gaseous medium flowing througl'r 'the duct. i

9. A prime mover comprising a rotor having a series of peripheral blades defining fluid passages, a stator coaxial with the rotor, the stator also having blades defining fluid passages, means defining a duct for delivering a combustible gaseous medium into the passages between 0 the stator blades, the blades of the stator and the rotor being shaped and dimensioned in accordance with the formula q+Aw 6 ART) So where Sp is the area of the entrance to the duct, and

S is the area of the chosen section,

whereby to insure isothermal expansion of the gaseous medium as it flows through the passages in the stator and rotor.

10. A prime mover comprising a rotor having -a. series of peripheral blades defining fluid passages, means defining stationary ducts from which an expansible fluid is delivered into said passages, said ducts being shaped and dimen- I sioned inaccordance with the formula where ,q is the quantity of heat communicated to the flowing gas from entrance section to chosen section,

A is the caloric equivalent of work,

So is the area of the entrance to the duct, and

' S is the area of the chosen section,

whereby to insure isothermal expansion of a burning gaseous medium flowing through said passages, and means for adding heating energy -to the gaseous medium as it flows through said passages.

11. In combination, in apparatus for use in the generation of power, means defining a duct through which a burning gaseous medium flows 20 toward a point of discharge, said duct being internally shaped and dimensioned in accordance with the formula a+Arz g is the acceleration due to gravity,

C0 is the mean velocity at the entrance to the nozzle,

R is the gas constant,

where T is the absolute temperature of the gas at the chosen section,

e is the base of the system of Napierian logarithms, v

m is the abscissa of the chosen section measured along the axis of the duct,

ga: is the quantity of energy transformed into heat by friction loss,

q is the quantity of heat communicated to the flowing gas from entrance section to: chosen section,

A is the caloric equivalent of work,

So is the area of the entrance to the duct, and

S is the area of the chosen section,

whereby to insure isothermal expansion of the burning gaseous medium passing through said duct, with concomitant increase in velocity, as it approaches the discharge point.

HENRY M. PU'I'MAN, JR.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 745,270 Wilkinson Nov. 24, 1903 864,315 Lentz Aug. 27, 1907 910,237 ,Schmick Jan. 19, 1909 2,225,311 Lysholm Dec. 17, 1940 2,242,767 Traupel May 20, 1941 2,243,467 Jendrassik May 27, 1941 2,377,611 Caldwell June 5, 1945 2,394,124 Warren Feb. 5, 1946 2,407,166 Kreitner et al Sept. 3, 1946 2,468,461 Price Apr. 26, 1949 FOREIGN PATENTS Number Country Date 232,681 Germany Mar. 18, 1911 339,590 Germany 'July 29, 1921 357,797 Germany Sept. 1, 1922 

